Automatic ammunition loading device



Feb. 19, 1957 Filed Jan. 15, 1949 J. G. SHONTS ET AL AUTOMATIC AMMUNITfON LOADING DEVICE 4 Sheets-Sheet l 2 \NVENTORS JAMES G. SHONTS SAMUEL H. TEPHENSON M I M ATTORNEY Feb. 19, 1957 Jie. SHONTS ETAL 2,781,596

AUTOMATIC AMMUNITION LOADING DEVICE Filed Jan. 15, 1949 4 Sheets-Sheet 2 \NVENTQRfi JAMES e. SHONTS SAMUEL H. STEPHENSON AT T0 RN EY Feb. 19, 1957 J. G. SHONTS ETAL 2,781,696

AUTOMATIC AMMUNITION LOADING DEVICE Filed Jan. 13, 1949 4 She ets-Sheet s INVENTOREJ JAMES 6. SHONTS SAMUEL H.,STEPHENSON BYMWM AT TO RN EX Feb. 19, 1957 J G. SHONTS ETAL AUTOMATIC AMMUNITION LOADING DEVICE 4 Sheets-Sheet 4 Filed Jan. 15, 1949 \NVENTORS JAMES G. SHONTS STEP EN SAMUEL H.

\l ETA UL v 5 iagurnw Un t d t lnents, tq, the ,Unitedstate's, of America as represented by the Secretary of the Navy xtipueitioii ninety 13, no, ee] No. 70,685

8' Claims; C1. iii-4s This inventionjrela'tes to improvements in, automatic loading mechanisms, and more particularly to loading devices which are adapted to provide free-flight delivery of rounds of ammunition into the breech of quick-firing guns.

,In'the. operation ofpanti-aircraft and other types of quick-firing guns,. itis desirable that a. ramming or loading devicelbe provided which will automatically deliver the individual rounds oftammunition to the breech of the gun at a rapid rate andin such a manner that nordamage to the. ramming device can result from premature or accidental closure of the breechblock, or from failure of the ramming device to retractitself out of the way of the reechblock. Interlock vsystems of various types have sometimes been employed with the view: of protecting the gun rammingmechanism from such damage, but these systems frequently fail to perform their intended function in theevent the damaging action of the breechblock begins before thevrar'nming mechanism is free and clear of the breech, particularlywhen the time interval between successive breech-loading operations must be reduced to a rniniihuml. Free-flightldelivery of each round ofammuni tioh into, the gun, on, the lo'therhand, doesnotrequire such close proidinity between the gun breech andranimer at the end of the iram'min'glstroke, thereby positively protecting the rairimingmechanism from possible damage whichmay resultfrommalfunctioning of'the'breechblock closing mechanism;' In additionto providing such positive protection for the ramming mechanism, free-flight delivery allows each round of ammunition to be delivered intothe breech in a sho'rter interval of timeand in such a manner that the accuracy of. the delivery operation will not be adverselyatfe'cted under arying conditions of pitch and roller gunelevatioti. It is also desirablethat thera i ming jrn'echanism be" emana ed and operated in sticfhja manner that it can be" reloaded 'while the gun is being firedfthereby'increa'sing the rapidity with which successive operating cycles can be performedf It therefore an imporitantiobject of the presjent inven tie to produce afully lauto'rn'aftief loading device f orf a' sfr t' a fre'e'fflight delivery? 55 into the gun breechin a t? i false ai eet??? t it? i j fie to i t ef ah" m t q ae eaimeehanism whi h. delivers c e r,

chron'ized closure of the breechblock or resultingI-from' failure- ,of, the loader actuator to retract'th'e loader'out of theway.

2,781,696 P eter 1 1195 ice loading mechanism which provides free-flight delivery of the round into the gun breech byco' mbined centrifugal and linear motion insuch a manner that the accuracy of the delivery operation is not adversely afi'ected by the presence of centrifugal forces acting on'the' round. f

It is a further, object of the instant invention to provide an automatic gun-loading mechanism movable along an arcu'ate ,path by a parallel linkage arrangement :in such a manner as to accelerate each round for free-flight delivery into the breech of the gun, the gun-loading mechanism also being'movable to a load receiving position parallel to but cribofaligmnent with the gun barrel; and being capable ofstarting the loading stroke during counterrecoihso that loading stroke is completed before the barrel hasreachedbattery positioin I Y A further object of this-invention is to produce alien age systeniincluding both main and auxiliary link g'e components-adapted to transform straight line motion into rotary motion and to impart a predetermined swinging movement" to a parallel linkage mechahism,'the auxiliary linkage syste'ni' being further adapted to *move the said main linkage component past the dead center pan ies? It is also an object of this: invention to provide projectile centering and holding means adapted to automatieallyactuated' by coacti'on with the' rini of each projectile as it is injectedfinto andejected froin the rain mer, case, thereby providing positivecentering" or niovementoftl'i'e p'rojectile'in'to and out of the automatic loading device. l v h f j Further objects are to provide a constructionio'f niuh1'sir'nplicity,-ecohorhy and ease (re ssembly and dis assembly, also su'ch'fu'rther objects, advantages and capa bilities as'will fully appearandjas are inherently possessed by' the deyic'eiaiidinvention'described'herein. U The invention further resides in the" combination; con-Q stiuc'tion and arrangement of parts illustrated inf the i accompanying'drawings, and while thereis showntherein a preferred embodiment thereof, it is to be understood that the same'is illustrative o'f'theinventio'n and that the invention isca'pable ofmodification and change and corn-j prehends other details of construction; without departing from the" spirit thereof or the scope of the appended claims.' V V Referringto the drajwingsz z figure: 1 lS a perspective view showing the loadet c en'ipty at the'load receiving o'sition 'and with the walking beanrrnechanism; swung forwarder v Figure Zis'aper spective View showing 'the' Figure 4 'is' a fronf'elevaticnal view assembly of Figures; 1 Figure 5' is a'bott'o'm seetional View assembly of Figure 3, showing the latch H V tion and the'cam toggle rollers in thedise'n'gagedposition.

re resh pa 1 Figure 6 is a fragmentary sectional view of the latch taken along the line VIVI in Figure 5.

Figure 7 is a bottom sectional view of the loader case assembly of Figure 3 showing the latch in the up position and the cam toggle rollers in the load engaging position.

Figure 8 is a fragmentary sectional view of the latch taken along the lines VIIIVIII in Figure 7.

Referring now more particularly to the drawings, in which like reference numerals indicate like parts in the several views, there is shown generally at 10 a loader case assembly, preferably of cylindrical shape, having one end 11 open and the opposite end closed by the buffer assembly 12. A rear support ring 13 is secured by welding or other suitable means to the loader case 14 in a position adjacent to the buffer assembly 12 and has aflixed thereto the diametrically opposed upper and lower trunnions 15 and 16 respectively. Another supporting ring 17 is similarly secured to the forward portion of the cylindrical case 14 and has an upwardly extending trunnion 18 aflixed thereto. Between the forward and rear support rings '17 and 13 is an intermediate support ring 19, also secured to the case 14 and having a downwardly extending trunnion 20 welded thereon.

The main drive arm 23 for the loader assembly 10 has one end 24 pivotally supported on the trunnion 18 of the forward support ring 17 and has a bifurcated yoke 25 at its opposite end which is pivotally supported by the bearing bolts 26 on the drive. arm support bracket 27 of the main support base 28. An actuator arm 29, preferably formed integral with the main drive arm 23, extends angularly outwardly therefrom and has a free end 30 pivotally attached by the pin 33 to one end of the walking beam 34, the latter being pivotally attached by the pin 35 to one end of a lever 36 whose opposite end is pivotally supported by the pin 37 on the bracket extensions 38 carried by the main support base 28. Thus, the walking beam 34 is free to rock about the pin 37 as a center, and has its other end pivotally connected by the pin 39 to a fitting 40, which is secured to the free end of the piston rod 43 of the servomotor or hydraulic actuator 44. The actuator 44 is pivotally supported by the transverse pinion 45 for free rocking movement within the bracket extensions 46 carried by the main support base 28, so that the linear motionof the piston rod 43 of the actuator 44 is converted into rotary motion by the walking beam 34 and linkage elements associated therewith. Thus, the fluid under pressure may be supplied to actuate the hydraulic cylinder 44 through suitable flexible tubing not shown, which communicates the cylinder 44 with an easily controlled fluid supply system of conventional design. The yoke 25 of the main drive arm 23 is keyed to the bearing bolt 26 on one side of the support bracket, and a short link member 47 has one end 48 keyed to the bolt 26 on the opposite side of the bracket 27. Pivotally attached by the pin 49 to the other end 50 of the link 47 is a drag link 51 having its opposite end 42 pivotally attached by the pin 52 to a short arm 53 keyed at its other end to the bolt 54, which is journalled in the supporting structure 41 for free turning movement therein. The other end of the bolt 54 is aflixed to the rear auxiliary drive arm 55, which has its free end 56 pivotally supported on the trunnion 15 carried by the ring 13. Although most of the torque required to move the loader case assembly 10 is imparted thereto through the main drive arm 23, a small portion of the driving torque is transmitted by the auxiliary drive arm to the case assembly 10 through the short link 47, the drag link 51, and bolt 54. The rear auxiliary drive arm 55 and associated linkage components also insure that all components of the entire linkage system follow through the dead center position in such a manner as to impart a smooth and uninterrupted swinging movement to the loader case assembly 10.

The lower support arm 57 has one end thereof pivotally supported on a trunnion 58 secured to the forward end of the aft support bracket 59, and the arm 57 has its other end 70 pivotally attached to the trunnion 20 of the intermediate support ring 19. Another lower support arm 62 has one end 71 pivotally attached to the lower trunnion 16 on the rear support ring 13, and has its other end secured to one arm 63 of the bell crank 64 which is pivotally supported on the aft support bracket 59 by the pin 65. The other arm 66 of the bell crank 64 carries a pin 61 having its free end swivelled in the free end 67 of the link member 68. The opposite end of the link member 68 is secured to a movable disposal conduit or case deflector chute 69 so as to laterally move the same in accordance with the movement of the bell crank 64 as it turns about the pin 65 as an axis. Thus, the main drive arm 23, the rear auxiliary drive arm 55, the lower support arms 57 and 62, form a parallel linkage arrangement adapted to support the loading case assembly 10 for a free swinging movement from the load receiving position illustrated in Figure 1 to the load delivering position at the end of each loading stroke as illustrated in Figure 2. An endless conveyor 72 having a plurality of cam controlled automatic clamping mechanisms 73' thereon preferably delivers individually in time sequence to the case assembly 10, when positioned as illustrated in Figure l, projectiles 21 or other rimmed cylindrical objects of substantially uniform length such as can flanged tubes, and the like. Upon the operation of suitable conventional sequence control or interlock devices, hydraulic fluid under pressure may be supplied to the actuator 44 so as to extend the piston rod 43 to exert a thrust on the main drive arm 23 and the auxiliary arm 55 so as to move the loading case assembly 10 to the delivery position at the end of the loading stroke as illustrated in Figure 2.

Figures 3 to 8 inclusive best illustrate the preferred form of construction for the toggle arm assembly 72 which is positioned on the loader case 14 between the open end 11 thereof and the forward support ring 17. The assembly 72 includes a three-segment, fixed collar 73 and a coacting sliding collar 74 which tends to move longitudinally along the loader case 14 toward the open end '11 thereof in accordance with the resilient pressure exerted by a compression spring 75 having one end 76 which seats in an annular shoulder 77 formed on the sliding collar 74 and another end '78 which coacts with the adjacent side 79 of the forward support ring 17. Three radially spaced apart support brackets 82 are secured to the fixed collar 73, the extensions 82' thereof being disposed on opposite sides of the three radially spaced apart oblong slots or apertures 83 which extend through the loader case 14 adjacent the open end 11 thereof. Pivotally supported by bolts 84 one on each pair of brackets 82 are the radially spaced apart cam toggle arms 85. One end of each of the toggle arms 85 supports a short pin 86 which serves as an axle for one of the toggle rollers 87. The opposite end of each of the toggle arms 85 has a notch 88 cut therein so as to coact with the edge of one of the apertures 83 when the toggle arms 85 are in the fully disengaged position shown in Figure 5, thereby allowing the cam trigger 89 to extend through the aperture 83 and into the interior of the loader case 14. A pin 90 disposed above each notch 88 pivotally attaches one end of each of the spaced apart links 92 to one of the toggle arms 85. The opposite end of each link 92 is pivotally attached by a pin 93 to one of the three radially spaced apart brackets 94 which are carried by the sliding collar 74. Whenever a closely fitting cylindrical rimmed object 21 is inserted into the loader case 14 with the toggle arms 85 in the fully cocked position illustrated in Figure 5, direct contact between the rim and the cam triggers 89 will uncock the toggle arms 85 by moving each of the pins 90 past the dead center position, thereby enabling the sliding collar 74 to move forward under action of the compression spring 75 so as to impart a pivotal movement simultaneously to all of the toggle arms 8 5, aboutthe bolts 'as axes. l n this manner the cam rollers STaie gradually depressed tlirough the apertires 83 so as to exert a resilieritipressureradially inward- 1y against the" exteriorsurface of the cylindrical object 2 1 inserted in the" loader case 14. Thepressur'e exerted by the rollers 87 ontlie surface of the object21 is applied sue'stsnfiany' nfamy by all of the rollers 87 to the coactin'g surface of the tapered or untapered cylindrical object 21 so that t'he latter is supported therebywith its axis substantially in alignment the longitudinal axis of the case 14; and" so tha'ta substantially uniform annu l'ar space is maintained between the interior surface 91 of the case 14 and the: exterior surface of the rimmed cylindrical objec't2'1 which is inserted therein:

\ Laterally. supportedbn the external surface'of the case 14" and'in a position between two of the three radially spaced ap'art toggle aifm s 72 is a fourth toggle arm assem bly 140,- which includes a link member 141 pivotally attached pin 14240" a bracket 143; which is carried by-the sliding. collar 74Qancl-alevel arm member 144 pivotally attached by the 145 to the fixedcollar 73. One end of arm member144 is pivotally attached to the link 141' bya pin 146, and the free end of the arm 144 rotatablysupports a centrifugal roller 147 which is adapted to be depressed into the cavity ql; of the case 14 through a fourth aperture 85" therein. When in the fully depressed position illustrated in Figure 7, the centrifugal roller 147 is toggled pa'st the 'deadecenter position in such a manner as to. maintain a predetermined spacing between the coactingisurface of the obje ct 21 and the adjacent interior surfa'ceof the case 14. Thus, the-to'ggle arm assembly 140 absorbs any thrust imposed upon it by thecentrifugal forces present when the loader case assembly 10 is moved to the delivery position illustrated in Figure 2, thereby preventingjvany centrifugal forces created by arcuate move; ment of-the object 21 from unequallyactuating-the toggle arm-assembly 72 in such Q'l'ljlfilllfllfil klSlO adversely affect the accuracy of the free-flight delivery of the rimobject 21} Whenever anobject 21 "is ejected from the loader case i 4,'the-tDgg1e 1 armassembly 1 40 is actuated by{ the coactingrim of the object sothatdtassumes-the position illustrated ll1- Flg-llfe5,'Wl1lCh"p0$lilOIlil$ maintained until the next' slidingmovernent of the collar 74 for the next loading cycle- 'is initiated-by' coa'ction between the rim of the object 21-- and i the cam triggers 89 of the ca m toggle arms 85.:- n

Preferably the hydraulic actuator 44 incorporates a hydraulic butting-means adapted to decelerate the swinging movement of the loader case assemblylll both in the loadreceivingposition illustrateddn Figure 1 and in theload-dischargingpositionillustrated in Figure 2; In thelatterposition-Abe forward movement of the; loader 'casel t 'is rapidly decelerated' ata predeterrnined' rate by the-"bufling aaction-of-=the hydraulic-actuator 44: with the resultthat-the object 21' movesforward} within the case ld -because: of its inertia-pas soon-as relative movement=ispermitted by release of the lateh assembly 22. The-1atch-22 is soconstructedand arranged as to engage with the' rim ofthe object 21 30 as-to hold the object Within-the case- 14 until i such dime asth'e bufiing' means for 'the hydra-ulic actuator-44*beginstodecelerate the forward movement" of the case -14'just-prior tocompletion ofthe loading '=or"delivery icyclez As the inertia' ofthe-object 2-1 carries it forward aftenthe case 14 comes torest,-. the rim of-the object-21 slides along the interior surface-91- of-the case -14-=withthertogglerollers 87 maintaining -the:-axis of the object 21="in substantial-- alignment with-the"longitudinal axis -of 1118"CElS6f 142 As' soon'as" the object 21-moves forward within the-interior cavity of the leases-14 m "the position-wherethe 'ri-rn of the object 21 engages "with the toggle rollers 87,' these rollers are caused to impart a pivotal-movement "to jthe oam toggle; arms .85 -topositionthe-. arms-85- and linkj: 92 --from-='flthfe;

uncooked positions; illustrated n; -Figitre- 7 to" the cockedpositionillustratedin-- Figure 5 thereby moving the sells? 24.3 th a e .19.. in,.,opa tid th seam t q' m ss qn spr n f i-t Thusa i' 55 toggle arm 35 r t P td n e andare: a tomat cally held by the spring 75 in the position required for the next loading or delivery cycle. N V

p The cam actuated latch assembly, 22 coacts with the rim of the object21 t o secure thisobject within the Case 14* until the" case assembly 10 has been positionedfor proper delivery and until such time as the buflin'g actio'n of the'hydraulic actuator 44' begins to deceleratewthe forward movemcnt of the case 14 as itapproaches thewdelivery position illustrated in FigureZ. A buffer 12,-'preferably of the fluid dampening type, is also incorporatedsin the closed" end of the case 14 o as'fltosabsorb the kinetic energy of the rimmed object 21 a s it comes, torest within the case 14. The bufier assembly 12 preferablyis constructed as an integral unit which maybe readily removed from thecase 14 for replacement or repair by, removing the attaching bolts 97. The bufier;12 prefegably is'formed by a corrugated rubber bellows 98; oheend of whichjs secured by rivets 100' to the inner surface ofjthe cupshaped member 99, and at .the other e'nd.80 thereof. the bellows 98 is secured to an interior rnernber 101 having an annular ring' 102 onv one side thereof adapted to form a fluid retaining well 103,within the bellows 98, which may be' filled with oil 104' or other suitablehydraulic fluid. An orifice rod ,or plunger 105,7secured to theiinte rior of the member 99 by 'the b'olt'106 has a conical frusturn' end portion107 of slightly smaller. diameter than the well 103 and is adapted'to coact' witl'r'the ring 102 to form an annular fluid dampcriirlg rec'es'soft substantially uniform predetermined configuration around the peripheryof the orifice plunger 105, If desired; the member 99 mayhave, cooling firis- 108. 011 the exterior surface thereof to' facilitate cooling-of the buffer 12, and may have an annular flange-109 thereonadapt'ed'tocoact with a sliding collar 110. A compression spring 111 interposed between the spaced apart annularrings- 112 and 113 which th'readedly engage with'the' members 99 and "101' respectively, tends at all-times to move the o'rie fice plunger out of fluid entrapping -er'i'gagement with the fluid Well 103 so that a maximum amount of fluid 104 will be present within the we'll 103 at the beginning of each-energy-absorbing cycle of the fluid dampening buffer 12; The isp'ring 11'1 therefor repositioris' the" buffera's s'rii bly 12 to its normal 3 position after each"buifingoperation has been coinplete'd'arid' the object 21 has"c'o'me to'rest within the case'14; whereupon "the rirnf of the"objec't"2l ceases to exert pressure upon the'coacting surface" 114 ofthe bulfer assembly. p The latch assembly 22 positively engage withth'e of the object'21 to secure the same within the case 14 throughout most of the delivery cycle anduntil the bufiing "means 'of the fluid actuator; begins "to decelerate the forwardmov'ernent of the case 14. The latch a'sf se'rhbly 22 includes a'cam follower ro'd'115 "slida'bl'y su'p ported within'ahousing 116 'afiixed'to the bottom of the case 14: One end ofthe rod carriei'sa roller 117 adapted'to coact with 'a cam quadra'nt 118 aflixed tothe" end 62" of the lower supportarm 57' whichdsjournalld on a trunnion 2i). Whenthe case-assembly 10"is"in"t h"e position illustrated'in'Figure 1,the cam q'uadfantllld is inthe positionshowhin'FigUre 8, and doesno'tc" n'tact the rollerll'i'to move the rod 115"'unt'il" theloaclih'g' or' delivery cycle'ofth'e case l4'ha'sfbeen substantially eomf ple'ted. Coaction between thequadrant 1'18 andthe rod 115. preferably occurs just'prior' 'to the" action ofthe bufiing means" of the actuator 44' in"dec'el'erating- 'the' forward movement" of the loaded case14." The portion 119 of the rod 115*furthest removed frorn theroller 117'v cam- 122; attached 'to' the outer extremity: thereof! The. washer 121 engages with the rodportion=119"ii "a"free 7 a sliding 'manner and the washer 121 is itself slidably iretained within the housing 116. An inner compression spring 123 exerts resilient pressure on the shoulder 120 and on the washer 121, thereby tending to force the washer 121 into contact with the abutting surface 125 of the cam 122 whenever the roller 117 is not in contact with the quadrant 118. The outer spring 124 exerts resilient pressure on the closed end 126 of the housing 116 and against the washer 121. A latch 127 is pivotally supported by the pin 128 in the horizontally disposed oblong slots 129 of the supporting member 139, and has a short arm 131 adapted to coact with the sliding cam 122 and a long arm 132 adapted to normally project itself upwardly into the cavity 31 of the case 14 through the aperture 133 formed in the bottom portion thereof. The torsion springs 134 have one end thereof secured to the fixed pins 135 and the other end thereof secured to the ends of the roller 136 so as to normally tend to force the long arm 132 of the latch 127 through the aperture 133 as shown in Figure 8. As the incoming rim of the object 21 slides past the latch 127, the long arm 132 thereof is depressed in opposition to the action of the torsion springs 134 until the rim passes over the latch and the object 21 is retained in place within the cavity 31 by locking engagement between the rim thereof and the vertical surface 137 of the arm 132, which position is maintained until the latch 127 is depressed in opposition to the action of the torsion springs 134 by coaction between the sliding cam 122 and the short arm 131 as illustrated in Figure 6. Rebound energy of the object 21 in striking the buffer 12 may readily be absorbed by the outer spring 124 without interference with the normal operation of the latch assembly 22, since the pins 128 which pivotally support the latch 127 are free to move along the oblong slots 129 and the short arm 131 thereof is free to slide the washer 121 within the housing 116 in opposition to the resilient action of spring 124. Such limited sliding movement of the latch 127 permits the absorption of substantial rebound energy without subjecting the latch assembly 22 to severe strain or adversely affecting its normal operation.

Operation In operation, the parallel linkage mechanism which supports the case 14 is moved to the position illustrated in Figure l by retracting the hydraulic actuator 44 so as to move the walking beam assembly 34 to its most forward position. The butting action of the hydraulic actuator 44 gradually decelerates the loader case 14 as it comes to rest in the load receiving position so as to avoid subjecting the component parts of the loading assembly to excessive shock loads. As soon as the loader case 14 has come to rest in the position illustrated in Figure 1, it is free to receive a round or other rimmed cylindrical object 21 from a suitable loading point such as an endless chain carrying automatic clamping devices which may release by cam or other suitable means as the round or other object 21 is transferred from the hoist conveyor to the loading or delivery assembly 107 Before each round is injected into the case 14, the cam toggle arms 85 are in the cocked-open position so as to readily receive the incoming round 21 from the hoist, as shown in Figure 5. If the rounds or other articles 21 to be delivered by the loader are of considerable length, each round preferably is engaged by a pair of automatic clamping devices, the first of which may be released at the beginning of the transfer operation by a suitable cam so as to allow the remaining engaged clamp to supply the thrust required to transfer the round to the loader case 14, the rim portion thereof being inserted into the loader case first. If desired, an independent emergency loader positive return mechanism may be provided to assure that the loader assembly is in the fully retracted position to receive the round 21 in the event the parallel linkage mechanism should for any reason fail to center position and cause the three rollers 87 carried by the toggle arms to contact the tapered or untapered exterior surface of the article 21 for supporting the same within the case 14 in a longitudinally slidable manner, while at the same time keeping the article 21 centered with its axis substantially concentric with the axis of the case 14 throughout the loading and unloading operations.

The automatic clamp on the chain hoist which remains engaged with the article 21 during the loading operation continues to drive the round 21 into the case 14 until completely released from clamping engagement by the suitable cam actuated clamp release mechanism forming part of the chain hoist assembly. During the final portion of the loading stroke, the round 21 continues to move under its own inertia until it strikes the buffer assembly 12 at the closed end of the case 14 where it strikes a latch 127 which engages with the rim of the article 21 to retain it in a position within the case 14. n its centered and last position within the case 14, the

round 21 begins its travel along a delivery path determined by the action of the parallel linkage supporting mechanism which is operated by torque supplied to the main and auxiliary drive arms by the hydraulic actuator 44 and its associated interconnecting linkage elements. During the delivery stroke of the loading assembly 10, the action of the compression spring tends to center the load 21 within the case 14 by exerting a thrust upon the sliding collar 74, the toggle arm bolts 84, and the toggle arms 85. However, during the first portion of the loader delivery stroke, the load 21 is subjected to rapid acceleration along an arcuate path, and the centrifugal forces which result tend to unbalance the normal centering action of the toggle arm assembly 72. The centrifugal force exerted by the round 21 during loading tends to force the round horizontally outwardly along the supporting drive arms and tends to disturb the normal centering action of the toggle arms which direct the round 21 along its free flight delivery course. This disturbing centrifugal action is therefore taken up by the fourth arm 140, which is toggled over the dead-center position during the loading operation so as to form a positive stop which eliminates the tendency of centrifugal action to disturb the normal alignment of the round 21 within the case 14.

At a predetermined point along the arc of travel for the loader delivery stroke, the actuator 44 ceases to apply additional loading power, and begins a bufling action which buffs the loader 10 to a stop at the end of its delivery stroke, at which time the center line of the case 14 is in alignment with the axis of the barrel, and the open end of the case is within the recoil area of the gun, but is not in sufiicient proximity to the breech to be damaged by inadvertent, unsynchronized movement of the breechblock. Just prior to the beginning of the buffing action of the actuator 44 near the end of the loading stroke, the cam roller 117 contacts the cam quadrant 118 carried by the lower forward support arm, thereby actuating the cam rod so as to depress the latch 127 to the position shown in Figure 6 so that the rimmed article 21 is free to move out of the case 14. Since the round 21 has been unlatched from the case 14 and has been accelerated to a relatively high linear velocity before the beginning of the bufiing operation, the round 21 will move out of the case 14 due to its own inertia, first along the guided flight course determined by the centralizing action of the toggle arm assembly 72, and secondly along a free-flight course leading into the breech of the gun. During the buifing operation, the three cam I toggle arms 72 exert equalized radial forces on the case of the round 21 as it leaves the case 14, thus supporting are-1.16%

collar 74' back, which rotates the anti-centrifugalforce toggle arm1144 upward, and at the same time energizes an interlock.v which causes hydraulic pressure to. be applied to the retract side of the hydi aulic actuator. to initiate the retraction stroke. The case deflector chute 69 is actuated by the return motion of the loading stroke to bring it into a position behind the breechblock but beyond the recoil area of the gun so as to receive the empty projectile case after the gun has been fired. Thus, the deflector chute 69 is actuated by the loading assembly in such a way that it will not interfere with the travel of the loader at any time. The loader assembly 10 is then retracted to the loading position by the actuator 44. The firing of the gun and ejection of the empty case into the chute 69 will automatically initiate a new loading stroke and sequence of delivery operation after :a new round 21 is properly latched in the case 14.

What is claimed is:

1. In combination with a gun having a breech adapted to receive a load having a rim thereon, a tubular loading case having a closed after end and an open forward end, means guiding said case for movement in an arcuate path from a load receiving position to a parallel load delivery position wherein said open end faces said breech, moving means including a servomotor accelerating said case along said path from said receiving position and then decelerating said case adjacent said delivery position to deliver the load into the breech by free flight delivery, load centering and supporting members resiliently carried by the loading case adjacent said forward end and actuated by the rim of the load to operative and inoperative positions, said members functioning in operative position to maintain the load in a predetermined aligned position Within the loading case during the loading stroke, and to direct the course of the load as it leaves the loading case under its own inertia for free flight delivery into the breech of the gun.

2. A device of the character described, comprising a case having a closed after end and an open forward end for receiving a cylindrical object having a rim at one end, parallel linkage mounting said case for movement in an arcuate path with its open forward end constantly facing in the same direction from a load receiving to a parallel load discharging position, a servomotor moving said case along said path means to automatically insert said object rim first into the said case from its open forward end when in the load receiving position, a releasable latch at said closed end coacting with said rim for releasably securing said object in said case, means adjacent said forward end centrally supporting said object within the said case during the movement thereof to the said discharging position, and a cam actuable to release said latch responsive to movement of said case toward said discharging position, said servornotor acting as buffing means to decelerate the movement of the said case at the load discharge end of the said arcuate path, whereby said object is discharged from said case for free flight delivery along a path directed by the said supporting means.

3. In a gun loading mechanism adapted to provide free flight delivery of rimmed-rounds into the breech of the gun by combined centrifugal and linear movement during each loading delivery stroke, the combination which comprises a tubular loading case having one of its ends open and its other end closed, a plurality of apertures in said case, a cam toggle arm pivotally mounted between its ends on said case adjacent each said aperture, a cam at one end of each of said toggle arms projecting into said case through said adjacent apertures when the toggle arms are in inoperative position rollers on the opposite ends of said toggle arms projecting; into. said case through a said apertures when said; tdggle arms: are in'. operative position, the rim. of each round alternately engaging" said earns and said rollers to move saidtogglearnisto operative and inoperative positions respectively, said toggle arms centering theround'in the loading,- case in operative position and directingthe-course of the roundv as it leaves said case, and means iinoluding resilient. means releasably holding said toggle arms in operative and inoperative positions.

4. The structure defined in claim 3 including a toggle arm having a round-engaging roller at one end thereof,

an aperture in said case through which said one end of' said last toggle arm may project into said case in operative position, and means connecting said last toggle arm to said first toggle arms for operation therewith to operative and inoperative positions, said last toggle arm resisting the tendency of centrifugal action to interfere with the normal centering action of the said cam toggle arms. during the load delivery stroke.

5. The structure defined in claim 3 including a releasable latch on said case adjacent the closed end thereof and engageable with the rim on the round to retainsaid round in said case during a portion of the loading delivery stroke.

6. In a gun loading mechanism adapted to provide free flight delivery of rimmed-rounds into the breech of the gun by combined centrifugal and linear movement during each loading delivery stroke, the combination which comprises a tubular loading case having one of its ends open and its other end closed, a plurality of apertures in said case, a cam toggle arm pivotally mounted between its ends on said case adjacent each said aperture, a cam at one 'end of each of said toggle arms projecting into said case through said adjacent apertures when the toggle arms are in inoperative position, the opposite ends of said toggle-arms projecting into said case through said apertures when said toggle arms are in operative position, the rim of each round alternately engaging said cams and said opposite ends of said toggle arms to move said toggle arms to operative and inoperative positions respectively, said toggle arms centering the round in the loading case in operative position and directing the course of the round as it leaves said case, and means including resilient means releasably holding said toggle arms in operative and inoperative positions.

7. In a gun loading mechanism adapted to provide free flight delivery of rimmed-rounds into the breech of the gun by combined centrifugal and linear movement during each loading delivery stroke, the combination which comprises a tubular loading case having one of its ends open and its other end closed, means mounting said case for movement in an arcuate path from a round receiving to a round discharging position, means to insert said round rim-first into said case when in the round receiving posi tion, a plurality of apertures in said case, a cam toggle arm pivotally mounted between its ends on said case adjacent each said aperture, a cam at one end of each of said toggle arms projecting into said case through said adjacent apertures when the toggle arms are in inoperative position, rollers on the opposite ends of said toggle arms projecting into said case through said apertures when said toggle arms are in operative position, the rim of said round upon insertion into the case engaging said cams to move said toggle arms to operative position, means for accelerating and then decelerating said mounting means to discharge said round from said case by free flight delivery, the rim of said round upon discharge from the case engaging said rollers to move said toggle arms to inoperative position, said toggle arms centering the round in the loading case in operative position and directing the course of the round as it leaves said case, and means including resilient means releasably holding said toggle arms in operative and inoperative positions.

References Cited in the file of this patent UNITED STATES PATENTS Brankston July 15, 1902 Schneider May 16, 1905 Kastner Oct. 1, 1912 McClain May 27, 1919 Schneider July 15, 1919 Lucht et a1. Apr. 5, 1938 Dabrasky et a1. June 1, 1948 

